KR102641642B1 - check valve - Google Patents

Abstract

Provides a check valve that can effectively suppress the occurrence of chattering. A check valve includes a housing provided with an inlet passage, a valve chamber, and an outlet passage, a seat member installed around the inlet passage and having a seat portion, a valve body that is pressed against the seat portion and blocks the inlet passage, and a valve body. A biasing member that presses toward the seat, a guide portion installed in the housing and guiding the valve body when moving in the axial direction of the valve body, and communicating with the valve chamber through a gap between the valve body and the guide portion, the axis of the valve body A damper chamber for attenuating directional movement force is provided, and the biasing member is disposed within the valve chamber.

Description

check valve

The present invention relates to a check valve provided in a flow path through which a fluid such as high-pressure gas flows.

Conventionally, check valves are installed in the middle of piping through which high-pressure gas flows to prevent high-pressure gas from flowing back. The check valve opens and closes due to the pressure difference between the upstream and downstream sides. If a check valve is installed in a place where pressure fluctuations occur rapidly, chattering is likely to occur due to repeated opening and closing in short cycles.

Therefore, as prior art regarding this type of check valve, there is, for example, a check valve provided with a damper that alleviates rapid movement of the valve body in the axial direction (see, for example, Patent Document 1). This check valve has a damper with a spring built into the valve body. The damper alleviates the sudden movement of the valve body, so even if valve vibration occurs, it is difficult to cause chattering where the valve body and the valve seat collide.

Japanese Patent Laid-Open No. 2012-140865

However, considering the chattering frequency of the valve body, it is desirable that the smaller the volume of the damper chamber, the greater the damping force. However, in the prior art check valve, in order to prevent an increase in pressure loss due to the presence of a spring, a spring is built into the damper chamber, thereby increasing the volume of the damper chamber. Therefore, the damping force is small.

Additionally, it is desirable that the larger the diameter of the damper chamber, the larger the damping force. However, in the prior art check valve, a damper chamber is provided inside the valve body and a spring is built into the damper chamber, so the diameter of the damper chamber is much smaller than the diameter of the pressure receiving surface of the valve body. . Therefore, the damping force is small at this point as well.

In this regard, in the check valve of the prior art, there are cases where chattering cannot be suppressed by effectively attenuating the moving force in the axial direction of the valve body in the damper chamber.

Therefore, the purpose of the present invention is to provide a check valve that can effectively suppress the occurrence of chattering.

In order to achieve the above object, a check valve according to the present invention includes a housing provided with an inlet flow path, a valve chamber, and an outlet flow path, a seat member installed around the inlet flow path and having a seat portion, and a pressure pressure applied to the seat portion. a valve body that blocks the inlet passage, a biasing member that presses the valve body toward the seat portion, and is installed in the housing, and when the valve body moves in the axial direction, a guide part that guides the valve body, and a damper chamber that communicates with the valve chamber through a gap between the valve body and the guide part to attenuate the axial movement force of the valve body, and the biasing member is in the valve chamber. It is placed.

According to this configuration, by disposing the biasing member that presses the valve body against the seat portion in the valve chamber, the volume of the damper chamber can be reduced and the diameter can be made large, and the damping force can be increased. Accordingly, the axial movement force of the valve body is attenuated by the large damping force of the damper chamber, and the occurrence of chattering can be effectively suppressed.

Additionally, the cross-sectional area of the damper chamber may be configured to be substantially the same as the cross-sectional area of the seat portion.

With this configuration, the occurrence of chattering can be effectively suppressed while maximizing the damping force by the valve body.

Additionally, the outlet flow path may extend from the valve chamber in the radial direction of the valve body.

With this configuration, the fluid flowing into the valve chamber flows out in the radial direction of the valve body. Therefore, the pressure loss caused by the fluid flowing in the valve chamber passing through the portion of the biasing member can be reduced.

Additionally, the valve body may be provided with a small diameter portion around the portion facing the outlet flow path.

With this configuration, the fluid entering the valve chamber flows smoothly from the space formed by the small diameter portion to the outlet passage extending in the radial direction of the valve body, thereby reducing pressure loss.

Additionally, an additional flow path may be further provided between the valve chamber and the damper chamber.

With this configuration, additional flow paths can be installed according to the size of the valve body or the damper effect desired in the damper chamber, thereby increasing stability by more appropriately controlling the flow rate of fluid entering and leaving the damper chamber.

Additionally, the shape of the pressure receiving surface in contact with the seat portion of the valve body may be formed in a cone shape widening from the upstream side toward the downstream side.

When configured in this way, the valve disc receives fluid pressure in the shape of a cone-shaped hydraulic surface. Accordingly, the lift amount of the valve body can be increased even with a small flow rate, making it difficult for the valve body to collide with the seat portion.

Additionally, the sheet portion may be formed so that its cross-sectional area increases from the upstream side to the downstream side.

With this configuration, changes in the flow rate of the fluid flowing from the inlet flow path to the valve chamber can be smoothed.

Additionally, the valve body may be provided with a through hole penetrating in a direction intersecting the axis direction of the valve body in a portion located in the valve chamber.

With this configuration, the area of the fluid passage from the valve chamber to the outlet passage increases, thereby reducing pressure loss due to fluid flow.

Additionally, a housing provided with an inlet flow path, a valve chamber, and an outlet flow path, a seat member provided around the inlet flow path and having a seat portion, a valve body that is pressed against the seat portion and blocks the inlet flow path, and the valve body. a biasing member that presses the valve body toward the seat portion; a guide portion that is installed in the housing and guides the valve body when the valve body moves in the axial direction; and a gap between the valve body and the guide portion that passes through the valve body. It may be provided with a damper chamber that communicates with the chamber and attenuates the axial moving force of the valve body, and the biasing member may be disposed in a biasing member chamber provided at a position opposite to the direction of the seat portion of the valve body.

According to this configuration, the biasing member that presses the valve body against the seat portion is disposed within the biasing member chamber, and the damper portion is made independent. Accordingly, the volume of the damper chamber can be reduced and the diameter can be increased, and the damping force can be increased. Therefore, the axial movement force of the valve body can be attenuated by the large damping force of the damper chamber, and the occurrence of chattering can be effectively suppressed.

According to the present invention, the damping force of the valve body can be increased by the damper chamber, and the occurrence of chattering can be effectively suppressed.

1 is a longitudinal cross-sectional view showing a first check valve according to a first embodiment of the present invention.
Figure 2 is a diagram showing a second check valve according to a second embodiment of the present invention, (A) is a longitudinal cross-sectional view, and (B) is a II-II cross-sectional view.
Figure 3 is a diagram showing a third check valve according to a third embodiment of the present invention, (A) is a longitudinal cross-sectional view, and (B) is a III-III cross-sectional view.
Figure 4 is a diagram showing a fourth check valve according to a fourth embodiment of the present invention, (A) is a longitudinal cross-sectional view, and (B) is a IV-IV cross-sectional view.
Figure 5 is a longitudinal cross-sectional view showing a fifth check valve according to a fifth embodiment of the present invention.
Figure 6 is a longitudinal cross-sectional view showing a sixth check valve according to a sixth embodiment of the present invention.
Figure 7 is a diagram showing a seventh check valve according to a seventh embodiment of the present invention, (A) is a longitudinal cross-sectional view, and (B) is a VII-VII cross-sectional view.
Figure 8 is a longitudinal cross-sectional view showing an eighth check valve according to an eighth embodiment of the present invention.
Figure 9 is a longitudinal cross-sectional view showing a ninth check valve according to a ninth embodiment of the present invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiment, an example will be described where the upward direction in the drawing is the inlet side, the left direction in the drawing is the outlet side, and the fluid G flows from upward to left. The concept of the up-down, left-right direction in the documents of this specification and patent claims coincides with the concept of the up-down, left-right direction in the state of the first check valve 1 shown in FIG. 1.

(First check valve according to the first embodiment)

1 is a longitudinal cross-sectional view showing a first check valve 1 according to the first embodiment. The first check valve 1 has a valve body 20 accommodated in a valve chamber 11 formed in the housing 10. The valve chamber 11 has a cylindrical cross section, and the valve body 20 of the cylindrical cross section moves in the vertical direction. The upward and downward direction of the valve body 20 is the axis direction. In the housing 10, an inlet flow path 12 is provided in the upper part of the valve chamber 11, and an outlet flow path 13 is provided in the left side of the valve chamber 11. The circumference of the inlet passage 12 that opens into the valve chamber 11 is the seat portion 14 that the valve body 20 contacts. According to this embodiment, the housing 10 also serves as a sheet member. The valve body 20 is pressed against the seat portion 14 and the inlet flow path 12 is blocked. In the first check valve 1, fluid G enters the valve chamber 11 from the inlet flow path 12 and exits in the left direction from the outlet flow path 13 extending in the radial direction of the valve body 20. .

In the valve body 20 of this embodiment, the pressure-receiving surface of the seal portion 22 that blocks the seat portion 14 is formed in a cone shape that widens from the upstream side through which the fluid G flows toward the downstream side. It is done. By making the shape of the pressure receiving surface of the valve body 20 conical, the lift amount of the valve body 20 is increased with a small flow rate. Accordingly, the valve body 20 is greatly separated from the seat portion 14 even if the fluid G flows at a small flow rate in a state in which the seal portion 22 is pressed against the seat portion 14 at a predetermined set pressure. Therefore, even if a small pressure fluctuation occurs in a state where the flow rate is small, it becomes difficult for the valve body 20 to collide with the seat portion 14. The set pressure is a pressure that presses the valve body 20 toward the seat portion 14 by the spring 15, which is a biasing member.

The valve body 20 has a large-diameter valve head 21 below the seal portion 22. A spring support portion 23 protruding in the radial direction is provided at the lower part of the valve head 21. Below the spring support portion 23, a circumferential portion 24 with a smaller diameter than the valve head 21 is provided.

On the other hand, the valve chamber 11 has a large diameter around the valve head 21 of the valve body 20. Below the valve chamber 11, a small-diameter guide portion 16 is provided to guide the circumferential portion 24 of the valve body 20 in the axial direction. Accordingly, a step portion 17 is formed between the large-diameter valve chamber 11 and the small-diameter guide portion 16. The valve body 20 is biased toward the seat portion 14 by a spring 15 installed in the step portion 17. The spring 15 is disposed within the valve chamber 11. The biasing member of this embodiment uses a compression coil spring that is preferably placed in the fluid G. In addition to the spring 15, the biasing member may use means such as other elastic bodies, magnetic springs, air springs, or pressing by electrostatic force.

The circumferential portion 24 of the valve body 20 enters the guide portion 16. Accordingly, the valve body 20 is guided by the guide portion 16 when moving in the axial direction. And, a damper chamber 30 is provided between the lower surface of the circumferential part 24 of the valve body 20 and the lower surface of the guide part 16 of the housing 10. The damper chamber 30 is installed on the side of the valve body 20 opposite to the seat portion 14 side. And, a connection passage 31 through which the fluid G enters and exits the damper chamber 30 is formed around the circumferential portion 24 and the gap S1 between the guide portion 16. The gap S1 of the connection passage 31 is set according to the setting value of the damping force. The gap S1 of the connection passage 31 may be, for example, on the order of several μm to several tens of μm. In the valve chamber 11, the gap S2 with the outer diameter of the valve body 20 is larger than the gap S1 between the connection passages 31. For example, the gap S2 may be three times or more than the gap S1.

The damper chamber 30 applies the force when the valve body 20 moves in the axial direction due to the resistance of the fluid G flowing in and out through the gap S1 of the connection passage 31, and the seat portion 14 and Attenuates on the opposite side. This damper chamber 30 can attenuate the axial movement force of the valve body 20 when the valve body 20 separates from the seat portion 14 and moves in the axial direction. Furthermore, by installing the damper chamber 30 in a direction opposite to the direction of the valve seat of the valve body 20, the axial movement force acting on the valve body 20 in the direction of the seat portion 14 can be directly attenuated. . Accordingly, the damper room 30 can obtain a large damping force.

Additionally, the diameter of the damper chamber 30 (damper diameter) is increased to the same extent as the diameter of the seat portion 14. Accordingly, the cross-sectional area of the damper chamber 30 is made substantially equal to the cross-sectional area of the seat portion 14, which is the pressure-receiving area of the valve body 20. Here, the range of values that can be taken for the cross-sectional area of the damper chamber 30 is 40% to 110% with respect to the pressure-receiving area of the valve body 20 (in the first check valve 1, the cross-sectional area of the seat portion 14). It's about %. Preferably it is 90% to 100%.

By making the cross-sectional area of the damper chamber 30 approximately equal to the cross-sectional area of the seat portion 14, which is the pressure-receiving area of the valve body 20, the damping force by the valve body 20 can be maximized. Then, the pressure of the fluid G acting on the valve body 20 in the direction of the seat portion 14 and the pressure of the fluid G acting in the direction of the damper chamber 30 become almost equal. In this way, the pressures of the fluid G acting in the axial direction of the valve body 20 cancel each other out, and the valve body 20 is stably biased toward the seat portion 14 by the biasing force of the spring 15. can do.

Furthermore, by flowing the fluid G flowing in the axial direction of the valve body 20 from the inlet flow path 12 to the outlet flow path 13 extending in the radial direction of the valve body 20, the fluid G Pressure loss as it passes through the part of the spring 15 can also be reduced.

In addition, the fluid G flowing into the valve chamber 11 from the seat portion 14 enters and exits the damper chamber 30 through the connection passage 31, and the gap between the valve chamber 11 and the valve body 20 is Since (S2) is made larger than the gap S1 of the connection flow path 31, the valve chamber 11 becomes a buffer section, and the valve chamber 11 is connected to the damper chamber 30 through the connection flow path 31. The pressure of the incoming and outgoing fluid (G) can be equalized.

In addition, since the spring 15 that biases the valve body 20 is disposed in the valve chamber 11, the volume of the damper chamber 30 can be reduced while its diameter can be increased. Therefore, the first check valve 1 can increase the damping force. For example, the maximum compression ratio of the volume of the damper chamber 30 can be increased to 2 or more to achieve a large damping force.

According to the first check valve 1 as described above, the diameter of the damper chamber 30 can be increased and the volume of the damper chamber 30 can be reduced. Therefore, according to the first check valve 1, the occurrence of chattering can be effectively suppressed by increasing the damping force by the damper chamber 30.

(Second check valve according to the second embodiment)

FIG. 2 is a diagram showing the second check valve 2 according to the second embodiment, where (A) is a longitudinal cross-sectional view and (B) is a II-II cross-sectional view. The second check valve (2) is further provided with an additional flow path (40) on the first check valve (1). In the following description, the same components as those of the first check valve 1 are given the same reference numerals, and the description thereof is omitted.

The second check valve 2 is further provided with an additional passage 40 between the valve chamber 11 and the damper chamber 30 through which the fluid G enters and exits the damper chamber 30. The additional passage 40 of the second check valve 2 is installed in the housing 10. A first flow path 41 is installed in the housing 10 in the direction from the valve chamber 11 to the lowest part of the damper chamber 30 in parallel with the guide part 16, and the lowest part of the first flow path 41 and the damper chamber (30) is connected to the second flow path (42). The additional flow path 40 of the second check valve 2 includes a first flow path 41 and a second flow path 42. By adjusting the cross-sectional area of the additional flow path 40, it is possible to configure a flow path of variable value through which the fluid G enters and exits the damper chamber 30. The cross-sectional area of the additional passage 40 can be set depending on the pressure of the fluid G or the size of the valve body 20, etc. By using the additional flow path 40, the amount of fluid G flowing into and out of the valve chamber 11 into the damper chamber 30 can be increased.

According to the second check valve 2, a variable value is added to the fixed value connection passage 31 formed between the guide portion 16 and the circumference of the circumferential portion 24 of the first check valve 1. The cross-sectional area of the flow path 40 is added. Since the configuration other than the second check valve 2 is the same as the first check valve 1, description of other configurations will be omitted.

According to the second check valve 2, the fluid G enters and exits the damper chamber 30 according to the pressure of the fluid G, the size of the valve body 20, the setting of the damper effect in the damper chamber 30, etc. The flow rate can be adjusted to an appropriate flow rate using the additional flow path 40. The second check valve 2 can also increase the diameter of the damper chamber 30 and reduce the volume of the damper chamber 30. Accordingly, the second check valve 2 also increases the damping force of the damper chamber 30, making it possible to effectively suppress the occurrence of chattering.

(Third check valve according to third embodiment)

FIG. 3 is a diagram showing the third check valve 3 according to the third embodiment, where (A) is a longitudinal cross-sectional view and (B) is a III-III cross-sectional view. The third check valve (3) has an additional flow path (50) different from the second check valve (2). In the following description, the same components as those of the second check valve 2 are given the same reference numerals, and the description thereof is omitted.

The third check valve 3 also has an additional passage 50 provided between the valve chamber 11 and the damper chamber 30 through which the fluid G enters and exits the damper chamber 30. The additional passage 50 of the third check valve 3 is provided in the valve body 20. In the valve body 20, a third flow path 51 is provided in the portion located in the valve chamber 11 from the outer periphery toward the axial center, and communicates with a fourth flow path 52 provided in the axial center of the valve body 20. I'm doing it. The fourth flow path 52 communicates with the damper chamber 30 at the lower end of the circumferential portion 24 of the valve body 20. The additional flow path 50 of the third check valve 3 includes a third flow path 51 and a fourth flow path 52. By adjusting the cross-sectional area of the additional passage 50, it is possible to configure a passage of variable value through which the fluid G enters and exits the damper chamber 30. The cross-sectional area of the additional flow path 50 can be set depending on the pressure of the fluid G or the size of the valve body 20, etc. By the additional flow path 50, the amount of fluid G flowing into and out of the valve chamber 11 into the damper chamber 30 can be increased.

According to the third check valve 3, a variable value is added to the fixed value connection passage 31 formed between the guide portion 16 and the circumference of the circumferential portion 24 of the first check valve 1. The cross-sectional area of the flow path 50 is added. Since the configuration other than the third check valve 3 is the same as the second check valve 2, description of other configurations will be omitted.

According to the third check valve 3, the fluid G enters and exits the damper chamber 30 according to the pressure of the fluid G, the size of the valve body 20, the setting of the damper effect in the damper chamber 30, etc. The flow rate can be adjusted to an appropriate flow rate using the additional flow path 50. The third check valve 3 can also increase the diameter of the damper chamber 30 and reduce the volume of the damper chamber 30. Accordingly, the third check valve 3 also increases the damping force by the damper chamber 30, making it possible to effectively suppress the occurrence of chattering.

(Fourth check valve according to the fourth embodiment)

FIG. 4 is a diagram showing the fourth check valve 4 according to the fourth embodiment, where (A) is a longitudinal cross-sectional view and (B) is a IV-IV cross-sectional view. The fourth check valve (4) has an additional flow path (60) different from the second check valve (2). In the following description, the same components as those of the second check valve 2 are given the same reference numerals, and the description thereof is omitted.

The fourth check valve 4 also has an additional passage 60 provided between the valve chamber 11 and the damper chamber 30 through which the fluid G enters and exits the damper chamber 30. The additional passage 60 of the fourth check valve 4 is installed in the guide portion 16. The guide portion 16 is provided with a fifth flow path 61 that communicates from the valve chamber 11 to the vicinity of the lowest part of the damper chamber 30. The additional flow path 60 of the fourth check valve 4 is provided with a fifth flow path 61. By adjusting the cross-sectional area of the additional flow path 60, it is possible to configure a flow path of variable value through which the fluid G enters and leaves the damper chamber 30. The cross-sectional area of the additional passage 60 can be set depending on the pressure of the fluid G or the size of the valve body 20, etc. By using the additional flow path 60, the amount of fluid G flowing into and out of the valve chamber 11 into the damper chamber 30 can be increased.

According to the fourth check valve 4, a variable value is added to the fixed value connection passage 31 formed between the circumference of the circumference 24 of the first check valve 1 and the guide portion 16. The cross-sectional area of the flow path 60 is added. Since the configuration other than the fourth check valve 4 is the same as the second check valve 2, description of the other configuration is omitted.

According to the fourth check valve 4, the fluid G enters and exits the damper chamber 30 according to the pressure of the fluid G, the size of the valve body 20, the setting of the damper effect in the damper chamber 30, etc. The flow rate can be adjusted to an appropriate flow rate using the additional flow path 60. The fourth check valve 4 can also increase the diameter of the damper chamber 30 and reduce the volume of the damper chamber 30. Accordingly, the fourth check valve 4 also increases the damping force by the damper chamber 30, making it possible to effectively suppress the occurrence of chattering.

(Fifth check valve according to the fifth embodiment)

Figure 5 is a longitudinal cross-sectional view showing a fifth check valve according to the fifth embodiment. The fifth check valve 5 has a different shape from the first check valve 1 and the valve seat 70. In the following description, the same components as those of the first check valve 1 are given the same reference numerals, and the description thereof is omitted.

The valve seat 70 of the fifth check valve 5 is formed to widen in a tapered shape from the inlet passage 12 toward the valve chamber 11. That is, the valve seat 70 is formed so that its cross-sectional area increases from the upstream side through which the fluid G flows toward the downstream side. The valve seat 70 may be formed curved so as to widen from the inlet passage 12 toward the valve chamber 11. Since other configurations of the fifth check valve 5 are the same as those of the first check valve 1, descriptions of the other configurations are omitted.

According to the fifth check valve 5 configured in this way, the change in flow rate of the fluid G flowing from the inlet passage 12 to the valve chamber 11 can be smoothed when the valve body 20 is opened. By smoothing the change in flow rate of the fluid G, the opening operation of the valve body 20 can also be smoothed. Here, since chattering suppression is the same as that of the first check valve 1, its description is omitted.

(6th check valve according to the 6th embodiment)

Fig. 6 is a longitudinal cross-sectional view showing the sixth check valve 6 according to the sixth embodiment. The shape of the valve body 80 of the sixth check valve 6 is different from that of the first check valve 1. In the following description, the same components as those of the first check valve 1 are given the same reference numerals, and the description thereof is omitted.

The valve body 80 of the sixth check valve 6 has a small diameter portion 85 provided at the valve head 81. The small diameter portion 85 is provided around the valve head 81 facing the outlet passage 13. Due to the small diameter portion 85, the middle portion of the valve head 81 in the axial direction has a small diameter. Due to this small diameter portion 85, the space of the valve chamber 11 in the portion of the outlet passage 13 is increased. Since other configurations of the sixth check valve 6 are the same as those of the first check valve 1, descriptions of the other configurations are omitted.

According to the sixth check valve 6 configured in this way, a large space can be secured by the small diameter portion 85 in the valve chamber 11 in the portion opposite to the outlet passage 13. Accordingly, the fluid G entering the valve chamber 11 flows smoothly from the space formed by the small diameter portion 85 to the outlet flow path 13 extending in the radial direction, thereby reducing pressure loss. Additionally, the weight of the valve head 81 of the valve body 80 is lightened by the small diameter portion 85. Accordingly, the center position of the valve body 80 moves in the direction of the peripheral portion 24. As the center position of the valve body 80 approaches the guide portion 16, lateral vibration of the valve body 80 is suppressed. Here, since chattering suppression is the same as that of the first check valve 1, its description is omitted.

(7th check valve according to the 7th embodiment)

Fig. 7 is a diagram showing the seventh check valve 7 according to the seventh embodiment, where (A) is a longitudinal cross-sectional view and (B) is a VII-VII cross-sectional view. The seventh check valve 7 has a different valve head 81 of the valve body 80 from the sixth check valve 6. In the following description, the same components as those of the sixth check valve 6 are given the same reference numerals, and the description thereof is omitted.

The seventh check valve 7 has a through hole 86 provided in the small diameter portion 85 of the valve head 81. The through hole 86 is provided in a direction intersecting the axial direction of the valve body 80. The through hole 86 in this embodiment is installed in a direction perpendicular to the axial direction of the valve body 80. As shown in Fig. 7(B), two through holes 86 are provided at 90° intervals in the circumferential direction of the small diameter portion 85, and communicate with each other at the axial center portion of the valve element 80. Since the other configuration of the seventh check valve 7 is the same as that of the sixth check valve 6, description of the other configuration is omitted.

According to the seventh check valve 7 configured in this way, in addition to the reduction of pressure loss due to the large space secured by the small diameter portion 85 like the sixth check valve 6, the valve is closed by the through hole 86. The passage area through which the fluid G flows from the chamber 11 to the outlet flow path 13 increases, thereby further reducing the pressure loss of the fluid flowing from the valve chamber 11 to the outlet flow path 13. . Here, since the suppression of chattering is the same as that of the sixth check valve 6, its description is omitted.

(Eighth check valve according to the eighth embodiment)

Fig. 8 is a longitudinal cross-sectional view showing the eighth check valve 8 according to the eighth embodiment. The structure of the seal part 22 and the seat part 18 of the valve head 81 of the valve body 80 of the eighth check valve 8 is different from that of the sixth check valve 6. In the following description, the same components as those of the sixth check valve 6 are given the same reference numerals, and the description thereof is omitted.

The 8th check valve 8 has the upper part of the valve head 81 provided with the seal part 82 of a planar shape. The seal portion 82 is provided on the outer periphery of the valve head 81, and a concave portion 87 is provided in the central portion. By providing the concave portion 87, the movement of the valve element 80 in the axial direction is stabilized. On the other hand, the seat portion 18 is formed in a plane perpendicular to the axial direction of the valve body 80. When the valve body 80 is biased toward the seat portion 18, the seal portion 82 of the valve head 81 is pressed against the seat portion 18 and the inlet passage 12 is blocked. Since other configurations of the eighth check valve 8 are the same as those of the sixth check valve 6, descriptions of other configurations are omitted.

According to the eighth check valve 8 configured in this way, the time and effort required for manufacturing the seal portion 82 and the seat portion 18 of the valve head 81 can be reduced. In addition, pressure loss can be reduced by the large space secured by the small diameter portion 85, like the sixth check valve 6. Here, since the suppression of chattering is the same as that of the sixth check valve 6, its description is omitted.

(Ninth check valve according to the ninth embodiment)

Fig. 9 is a longitudinal cross-sectional view showing the ninth check valve 9 according to the ninth embodiment. Here, the same components as those of the first check valve 1 will be described by assigning the same symbols. The ninth check valve 9 has a valve body 90 accommodated in a valve chamber 11 formed in the housing 10. The valve chamber 11 has a cylindrical cross section, and the valve body 90 of the cylindrical cross section moves in the vertical direction. The upward and downward direction of the valve body 90 is the axis direction. In the housing 10, an inlet flow path 12 is provided in the upper part of the valve chamber 11, and an outlet flow path 13 is provided in the left side of the valve chamber 11. The area around the opening of the inlet passage 12 to the valve chamber 11 is the seat portion 14 that the valve body 90 comes into contact with. The valve body 20 is pressed by the seat portion 14 and blocks the inlet passage 12. In the ninth check valve 9, the fluid G enters the valve chamber 11 through the inlet flow path 12 and exits in the left direction through the outlet flow path 13 extending in the radial direction of the valve body 90. .

In the valve body 90 of this embodiment, the pressure-receiving surface of the seal portion 92 that blocks the seat portion 14 is formed in a cone shape that widens from the upstream side through which the fluid G flows toward the downstream side. By making the pressure receiving surface of the valve body 90 conical, the lift amount of the valve body 90 is increased with a small flow rate.

The valve body 90 is a valve head 91 located below the seal portion 92. The valve head 91 is provided with a small diameter portion 95 whose diameter is smaller than the outer diameter of the seal portion 92. At the lower part of the small diameter portion 95, a sunshade-shaped protrusion 93 is provided that protrudes in the radial direction. Below the shade-shaped protrusion 93, a peripheral portion 94 with a smaller diameter than the small diameter portion 95 of the valve head 21 is provided.

On the other hand, the valve chamber 11 has a large diameter around the valve head 91 of the valve body 90. Below the valve chamber 11, a damper portion 19 of medium diameter is installed. The damper portion 19 is installed in the range where the sunshade-shaped protrusion 93 moves in the axial direction. Below the damper portion 19, a small-diameter guide portion 16 is provided to guide the circumferential portion 94 of the valve body 90 in the axial direction. Accordingly, a step portion 17 is formed between the medium diameter damper portion 19 and the small diameter guide portion 16.

The circumferential portion 94 of the valve body 90 enters the guide portion 16. Accordingly, the valve body 90 is guided by the guide portion 16 when moving in the axial direction. A spring chamber 35 is provided between the lower surface of the circumferential part 94 of the valve body 90 and the lower surface of the guide part 16 of the housing 10. The spring seal 35 is an additional flow path ( 40) is in communication with the valve chamber (11). The spring 15 is a compression coil spring and is disposed in the spring chamber 35. The fluid in the spring chamber (35) is discharged to the valve chamber (11) through the additional flow path (40). The valve body 90 is biased toward the seat portion 14 by a spring 15 installed in the spring chamber 35.

In addition, a damper chamber 30 is provided between the lower surface of the shade-shaped protrusion 93 of the valve body 90 and the step portion 17 formed between the damper portion 19 and the guide portion 16. . The damper chamber 30 is installed in the middle portion of the valve body 90 in the axial direction. A first connection passage 32 through which the fluid G enters and exits the damper chamber 30 is formed between the perimeter of the shade-shaped protrusion 93 and the damper portion 19. The first connection passage 32 is formed by a gap S3. A second connection flow path 33 is formed between the circumferential portion 94 of the valve body 90 and the guide portion 16. The second connection passage 33 is formed by a gap S1. The gap (S3) is larger than the gap (S1). In other words, the relationship is S3 > S1. The gap S3 and the gap S1 are set according to the setting value of the damping force. For example, the gap S1 may be on the order of several μm to several tens of μm. The gap S3 may be, for example, about 1.5 times the gap S1.

The damper chamber 30 has a seat portion ( 14) It is possible to attenuate the axial movement force when moving away from the axial direction. Furthermore, the damper chamber 30 can directly attenuate the axial movement force acting on the valve body 90 in the direction of the seat portion 14. Accordingly, the damper room 30 can obtain a large damping force.

In addition, according to this embodiment, the diameter of the damper chamber 30 (damper diameter) is made larger than the diameter of the seat portion 14, but the cross-sectional area of the damper chamber 30 is the seat portion which is the hydraulic pressure area of the valve body 90. It is almost equal to the cross-sectional area of the part 14. Here, the range of the value that can be taken for the cross-sectional area of the damper chamber 30 is 40% to 110% of the pressure-receiving area of the valve body 90 (in the ninth check valve 9, the cross-sectional area of the seat portion 14). That's about it. Preferably 90% to 100% is good.

By making the cross-sectional area of the damper chamber 30 approximately equal to the hydraulic pressure area of the valve body 90, the damping force by the valve body 90 can be maximized. Then, the pressure of the fluid G acting in the direction of the seat portion 14 with respect to the valve body 90 and the pressure of the fluid G acting in the direction of the damper chamber 30 become almost equal. In this way, the pressures of the fluid G acting in the axial direction of the valve body 90 cancel each other out, and the valve body 90 is stably biased toward the seat portion 14 by the biasing force of the spring 15. can do.

Furthermore, the fluid G flowing in the axial direction of the valve body 90 from the inlet flow passage 12 is directed to the radius of the valve body 90 in the wide space formed by the small diameter portion 95 of the valve head 91. By flowing through the outlet flow path 13 extending in this direction, the pressure loss of the fluid G can also be reduced.

According to the ninth check valve 9 as described above, the diameter of the damper chamber 30 can be increased and the volume of the damper chamber 30 can be reduced. Therefore, according to the ninth check valve 9, the damping force by the damper chamber 30 can be increased, and the occurrence of chattering can be effectively suppressed.

(General)

As described above, according to the check valves 1 to 9, at the stage when the valve head 21 of the valve body 20 falls from the seat portion 14, the damper chamber 30, which has a small volume and a large diameter, moves along the axis. Directional movement force can be effectively attenuated. Therefore, chattering of the valve body 20 can be effectively suppressed.

By suppressing the occurrence of chattering, valve vibration of the check valves 1 to 9 and valve collision due to vibration can be suppressed. By suppressing valve collision, the durability of the component parts (valve body 20, seat member (member provided with the seat portion 14), spring, etc.) of the check valves 1 to 9 can be improved. In addition, it is possible to reduce the pulsation or vibration of the connecting pipe due to valve vibration and the impact on other connected devices.

Therefore, according to the check valves 1 to 9, in addition to the check valve built into the control valve for the gas tank, hydraulic equipment, pneumatic equipment, and various other devices having a flow path through which fluid G including liquid such as gas and water other than gas flows. In plant control, etc., it becomes possible to effectively suppress chattering in the check valves 1 to 9.

(Other variations)

In the above-described embodiment, the valve element 20 is an example, and the shape of the connection flow path 31 and the additional flow paths 40, 50, and 60 can be changed depending on the setting of the damping force of the damper chamber 30. For example, a plurality of additional flow passages 40 and 60 may be provided around the guide portion 16. This configuration is not limited to the above embodiment.

In addition, the above-described embodiment represents an example, and various changes are possible without impairing the gist of the present invention. It is also possible to combine the configurations of each embodiment, and the present invention is not limited to the above-described embodiments.

1: first check valve
2: Second check valve
3: Third check valve
4: Fourth check valve
5: Fifth check valve
6: sixth check valve
7: Seventh check valve
8: Eighth check valve
9: Ninth check valve
10: Housing
11: valve room
12: Inlet flow path
13: outlet flow path
14: Seat part
15: Spring (no force)
16: Guide part
19: Damper part
20: valve body
21: valve head
24: Wonjubu
30: Damper room
31: Connection path
35: Spring room (tax free room)
40: Additional Euros
41: 1st Euro
42: Second Euro
50: Additional Euros
51: Third Euro
52: 4th Euro
60: Additional Euros
61: 5th Euro
70: Valve seat (seat part)
80: valve body
85: blind man
86: Through hole
90: valve body
91: valve head
95 Shade-type protrusion
S1: gap
S2: gap
G: fluid

Claims (9)

A housing in which an inlet flow path, a valve chamber, and an outlet flow path are installed,
a sheet member provided around the inlet passage and including a sheet portion;
A valve body that is pressed against the seat portion and blocks the inlet passage,
A valve head installed on the inlet flow path side,
A circumferential portion installed on the opposite side of the inlet passage,
a valve body installed between the valve head and the circumferential portion and including a spring support portion having a larger diameter than the circumferential portion;
a spring external to the circumference and connected to the spring support, and pressing the valve body toward the seat;
a guide portion installed in the housing and guiding the valve body when the valve body moves in an axial direction;
A damper chamber communicates with the valve chamber through a gap between the valve body and the guide portion and attenuates the axial movement force of the valve body,
The spring is disposed in the valve chamber,
The cross-sectional area of the damper chamber is 90% to 100% of the hydraulic pressure area of the valve body, which is the cross-sectional area of the seat portion in contact with the valve body,
A check valve, characterized in that the maximum compression ratio of the volume of the damper chamber is 2 or more. According to paragraph 1,
A check valve, characterized in that the outlet flow path extends from the valve chamber in a radial direction of the valve body. According to paragraph 2,
A check valve, wherein the valve body has a small diameter portion around a portion opposing the outlet passage. According to any one of claims 1 to 3,
A check valve, characterized in that an additional flow path is further installed between the valve chamber and the damper chamber. According to any one of claims 1 to 3,
A check valve, wherein the valve body has a pressure-receiving surface in contact with the seat portion formed in a cone shape widening from the upstream side to the downstream side. According to any one of claims 1 to 3,
A check valve, characterized in that the seat portion is formed so that the cross-sectional area increases from the upstream side to the downstream side. According to any one of claims 1 to 3,
A check valve characterized in that the valve body is provided with a through hole penetrating in a direction intersecting the axis direction of the valve body in a portion located in the valve chamber. delete delete